US20180073367A1 - A rotor for an electricity generator - Google Patents

A rotor for an electricity generator Download PDF

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Publication number
US20180073367A1
US20180073367A1 US15/558,922 US201615558922A US2018073367A1 US 20180073367 A1 US20180073367 A1 US 20180073367A1 US 201615558922 A US201615558922 A US 201615558922A US 2018073367 A1 US2018073367 A1 US 2018073367A1
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Prior art keywords
hub
blades
diameter
rotor
widest part
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Abandoned
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US15/558,922
Inventor
Peter John Murdoch
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Mako Turbines Pty Ltd
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Mako Turbines Pty Ltd
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Priority claimed from AU2015900950A external-priority patent/AU2015900950A0/en
Application filed by Mako Turbines Pty Ltd filed Critical Mako Turbines Pty Ltd
Assigned to MAKO TURBINES PTY. LTD. reassignment MAKO TURBINES PTY. LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ELEMENTAL ENERGY TECHNOLOGIES LIMITED
Assigned to ELEMENTAL ENERGY TECHNOLOGIES LIMITED reassignment ELEMENTAL ENERGY TECHNOLOGIES LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MURDOCH, PETER JOHN
Publication of US20180073367A1 publication Critical patent/US20180073367A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
    • F03B3/04—Machines or engines of reaction type; Parts or details peculiar thereto with substantially axial flow throughout rotors, e.g. propeller turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • F01D5/147—Construction, i.e. structural features, e.g. of weight-saving hollow blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
    • F03B13/12—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy
    • F03B13/26—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using tide energy
    • F03B13/264—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using tide energy using the horizontal flow of water resulting from tide movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B17/00—Other machines or engines
    • F03B17/06—Other machines or engines using liquid flow with predominantly kinetic energy conversion, e.g. of swinging-flap type, "run-of-river", "ultra-low head"
    • F03B17/061—Other machines or engines using liquid flow with predominantly kinetic energy conversion, e.g. of swinging-flap type, "run-of-river", "ultra-low head" with rotation axis substantially in flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
    • F03B13/10—Submerged units incorporating electric generators or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2220/00—Application
    • F05B2220/30—Application in turbines
    • F05B2220/32—Application in turbines in water turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/30—Energy from the sea, e.g. using wave energy or salinity gradient

Definitions

  • the present invention relates to a rotor for an electricity generator.
  • the invention has been primarily developed for use in a rotor for a hydro-powered electricity generator.
  • Such generators are used to convert kinetic energy from flowing fluids, such as water and wind, to electrical power.
  • Kinetic energy in flowing fluids is a known alternative to energy sources such as bio-fuels and fossil fuels for generating power.
  • energy sources such as bio-fuels and fossil fuels for generating power.
  • bio- and fossil fuels which, when used in electrical power generation, go hand-in-hand with emission of harmful combustion gasses into the atmosphere, generation of power by using flowing fluids has no or very little adverse effects on the atmosphere.
  • Known hydro-powered electricity generators typically have a rotor comprising a central hub to which is attached two or more outwardly extending blades.
  • the rotor is connected by a drive shaft to a rotary work to electrical power converter (i.e. a generator). Fluid flowing past the rotor blades causes it to rotate which in turn causes the rotation in the converter and the generation of electrical power.
  • a rotary work to electrical power converter i.e. a generator
  • Known rotors have a relatively small diameter hub and relatively long and slender blades.
  • the blades also have a relatively high aspect ratio (being the ratio of the blade length to the blade width).
  • Such blades are prone to high operating loads and subject to extreme bending moments in turbulent fluid flow. This typically results in broken blades.
  • the present invention provides a rotor for a hydro-powered electricity generator, the rotor including:
  • the ratio between the diameter of the tips of the blades to the diameter of the widest part of the hub is between about 1.2:1 and 2:1.
  • the ratio between the diameter of the tips of the blades to the diameter of the widest part of the hub is about 1.5:1 or 1.6:1.
  • the diameter of the tips of the blades is between 3.6 and 4.8 metres and the diameter of the widest part of the hub is 2.4 metres.
  • the diameter of the tips of the blades is between 30 and 32 metres and the diameter of the widest part of the hub is 20 metres.
  • the profile radius of the hub surface, in the region where each of the blade roots are mounted to the hub, is preferably between 1 ⁇ 6th of and equal to the radius of the widest part of the hub.
  • FIG. 1 is a front view of a first embodiment of a rotor
  • FIG. 2 is a perspective view of the rotor shown in FIG. 1 with stream lines;
  • FIG. 3 is cross sectional side view of a hydro-powered electricity generator with a second embodiment of a rotor.
  • FIGS. 1 and 2 show a rotor 10 for a hydro-powered electricity generator suitable for installation in a tidal flow environment.
  • the rotor 10 includes a hub 12 with a circular cross sectional shape and a longitudinal rotational axis 14 .
  • the rotor 10 also includes 7 equiangularly spaced apart blades 16 .
  • the hub 10 is formed from glass reinfornced plastic (GRP) or metal skins and the blades 16 are formed from carbon fibre metal composites.
  • GRP glass reinfornced plastic
  • Each of the blades 16 has a proximal root 16 a and distal tip 16 b.
  • Each of the blades 16 are mounted to the hub 14 , at their roots 16 a, at the widest part of the hub 14 .
  • the diameter of the widest part of the hub 14 is shown as diameter D 1 .
  • the diameter of the tips 16 b of the blades 16 is shown as diameter D 2 .
  • the ratio between diameters D 2 :D 1 is about 1.4:1.
  • FIG. 2 shows the rotor 10 relative to fluid flow stream lines 18 which demonstrate that as the fluid flows around the hub 12 its velocity increases. As the fluid accelerates and the local velocity increases, the local pressure decreases. This pressure reduction causes the fluid to remain concentrated around the hub 12 . As a result, the energy in a free stream of the fluid is concentrated in the region of the blades 16 .
  • the relatively large hub diameter D 1 advantageously serves the dual function of: 1. concentrating the energy in the passing water stream; and 2 supporting a relatively greater number of smaller and stronger blades 16 , which each have a lower aspect ratio.
  • the bending moment at the root is a function of the aspect ratio of the blade.
  • a blade with an aspect ratio of 8:1 will have a stress value in the root that is 16 times higher than the same blade with an aspect ratio of 4:1.
  • the blades can only have a limited chord length at the root due to the diameter restriction of the hub. This restriction of chord length means that the blade root thickness must be increased, to provide sufficient strength, over that otherwise required for an ideal foil section.
  • a relatively longer blade mounted to a relatively smaller hub also results in a lower apparent velocity for a given RPM and a lower torque radius.
  • the configuration of the rotor 10 i.e. relatively larger hub 14 , relatively shorter blades 16 , relatively large number of blades 16 ) redirects and concentrates the fluid flow in the inner 2 ⁇ 3 region and accelerates it through the outer 1 ⁇ 3 rd region where 100% of the power can be extracted. This advantageously means that the blades 16 are operating at maximum capacity, while also experiencing a lower stress loading.
  • the D 2 :D 1 ratio of the rotor 10 places the blades 16 in a zone of acceleration around the hub 12 with an ideal blade length for the blades 16 to operate in that zone. If the blades are too long relative to the hub diameter then the blades tips instead operate in a region with no fluid acceleration and therefore do not contribute positive torque.
  • FIG. 3 shows a hydro-powered electricity generator 30 with a second embodiment of rotor 32 .
  • the rotor 32 has a hub 34 and ten blades 36 .
  • FIG. 3 also shows blade root mounting beams 38 , a blade mounting hub 40 , a fixed main spindle 42 , a drive shaft 44 , a gear box 46 , a support beam 48 , a water seal 50 , bearings 52 and a rotary electrical generator 54 .
  • the beam 48 is used to connect the generator 30 to a floating deployment rig (not shown).
  • radius R being the profile radius hub 34 in the region where the hub 34 and the blades 36 are connected.
  • the radius R is 1 ⁇ 6 the radius of the hub 34 . This particular ratio maximises flow acceleration while avoiding turbulence.
  • One preferred form of the generator 30 has the following specifications:
  • Hub diameter D 1 2.4 meters
  • Blade tip diameter D 2 4.8 to 3.6 meters
  • Power generation range 50 to 300 kWs
  • Blade tip diameter to hub diameter ratio 2:1 to 1.5:1
  • Another preferred form of the generator 30 has the following specifications:
  • Blade tip diameter D 2 32 to 30 meters
  • Power generation range 0.5 to 5 MWs
  • Blade tip diameter to hub diameter ratio 1.6:1 to 1.5:1
  • the energy in the fluid stream is concentrated and accelerated across a set of small blades, which improves the efficiency of the rotor.
  • the total volume of the multiple (e.g. 7) smaller blades is less than the volume of a small number of (e.g. 3) large blades, which lowers manufacturing cost.
  • the smaller blades have a lower aspect ratio, which equates to a lower bending moment in the blade root, and a lower probability of blade breakage.
  • the incident velocity and the incident angle of the flow onto the smaller blades is closer to a uniform value across the span of the blades. This equates to near zero twist in the blade across its span, and allows the blades to be articulated in pitch control without any performance losses induced by blade twist.
  • the ability to adjust the pitch during operation means the rotor can be run at a constant rpm independent of the flow stream velocity. This allows the generator to be run at a constant rpm connected directly to the electrical grid thereby negating the cost of an electrical frequency inverter drive system.
  • rotors operating in fast flowing tidal flows are subject to high levels of turbulence in the stream.
  • the action of the flow acceleration of the water around the larger hub reduces the level of turbulence into the blade region. This improves the survivability of the blades in highly turbulence environments.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Oceanography (AREA)
  • Power Engineering (AREA)
  • Architecture (AREA)
  • Hydraulic Turbines (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)

Abstract

A rotor (10) for a hydro-powered electricity generator. The rotor (10) includes a hub (12) and a plurality of blades (16). The hub (12) has a circular cross sectional shape and a longitudinal rotational axis (14). The plurality of blades (16) each have a proximal root (16 a) and a distal tip (16 b). Each of the blade roots (16 a) are mounted to the hub (12) at the widest part thereof (D1). The ratio between the diameter of the tips (16 b) of the blades to the diameter of the widest part (D1) of the hub (12) is less than about 2:1.

Description

    FIELD OF THE INVENTION
  • The present invention relates to a rotor for an electricity generator.
  • The invention has been primarily developed for use in a rotor for a hydro-powered electricity generator. Such generators are used to convert kinetic energy from flowing fluids, such as water and wind, to electrical power.
    • BACKGROUND OF THE INVENTION
  • Kinetic energy in flowing fluids, such as water and wind, is a known alternative to energy sources such as bio-fuels and fossil fuels for generating power. Unlike, for example, bio- and fossil fuels which, when used in electrical power generation, go hand-in-hand with emission of harmful combustion gasses into the atmosphere, generation of power by using flowing fluids has no or very little adverse effects on the atmosphere.
  • Known installations for harvesting wind power generally have low running costs, however they tend to be expensive to install and have relatively low generation capacity. Known installations for harvesting hydropower, for example tidal power, on the other hand, have relatively higher generation capacity.
  • Known hydro-powered electricity generators typically have a rotor comprising a central hub to which is attached two or more outwardly extending blades. The rotor is connected by a drive shaft to a rotary work to electrical power converter (i.e. a generator). Fluid flowing past the rotor blades causes it to rotate which in turn causes the rotation in the converter and the generation of electrical power.
  • Known rotors have a relatively small diameter hub and relatively long and slender blades. The blades also have a relatively high aspect ratio (being the ratio of the blade length to the blade width). Such blades are prone to high operating loads and subject to extreme bending moments in turbulent fluid flow. This typically results in broken blades.
    • OBJECT OF THE INVENTION
  • It is an object of the present invention to substantially overcome, or at least ameliorate, the above disadvantage.
    • SUMMARY OF THE INVENTION
  • In a first aspect, the present invention provides a rotor for a hydro-powered electricity generator, the rotor including:
      • a hub with a circular cross sectional shape and a longitudinal rotational axis,
      • a plurality of blades, each having a proximal root and a distal tip, each of the blade roots being mounted to the hub at the widest part thereof,
      • wherein the ratio between the diameter of the tips of the blades to the diameter of the widest part of the hub is less than about 2:1.
  • Preferably, the ratio between the diameter of the tips of the blades to the diameter of the widest part of the hub is between about 1.2:1 and 2:1.
  • Preferably, the ratio between the diameter of the tips of the blades to the diameter of the widest part of the hub is about 1.5:1 or 1.6:1.
  • In one embodiment, the diameter of the tips of the blades is between 3.6 and 4.8 metres and the diameter of the widest part of the hub is 2.4 metres.
  • In another embodiment, the diameter of the tips of the blades is between 30 and 32 metres and the diameter of the widest part of the hub is 20 metres.
  • The profile radius of the hub surface, in the region where each of the blade roots are mounted to the hub, is preferably between ⅙th of and equal to the radius of the widest part of the hub.
    • BRIEF DESCRIPTION OF THE DRAWINGS
  • Preferred embodiments of the invention will now be described, by way of examples only, with reference to the accompanying drawings in which:
  • FIG. 1 is a front view of a first embodiment of a rotor;
  • FIG. 2 is a perspective view of the rotor shown in FIG. 1 with stream lines; and
  • FIG. 3 is cross sectional side view of a hydro-powered electricity generator with a second embodiment of a rotor.
    •  DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
  • FIGS. 1 and 2 show a rotor 10 for a hydro-powered electricity generator suitable for installation in a tidal flow environment. The rotor 10 includes a hub 12 with a circular cross sectional shape and a longitudinal rotational axis 14. The rotor 10 also includes 7 equiangularly spaced apart blades 16. The hub 10 is formed from glass reinfornced plastic (GRP) or metal skins and the blades 16 are formed from carbon fibre metal composites.
  • Each of the blades 16 has a proximal root 16 a and distal tip 16 b. Each of the blades 16 are mounted to the hub 14, at their roots 16 a, at the widest part of the hub 14. The diameter of the widest part of the hub 14 is shown as diameter D1. The diameter of the tips 16 b of the blades 16 is shown as diameter D2. In the embodiment shown, the ratio between diameters D2:D1 is about 1.4:1.
  • FIG. 2 shows the rotor 10 relative to fluid flow stream lines 18 which demonstrate that as the fluid flows around the hub 12 its velocity increases. As the fluid accelerates and the local velocity increases, the local pressure decreases. This pressure reduction causes the fluid to remain concentrated around the hub 12. As a result, the energy in a free stream of the fluid is concentrated in the region of the blades 16.
  • Another way of describing the above D2:D1 ratio is that the diameter of the hub 12 is relatively large compared to the length of the blades 16. The relatively large hub diameter D1 advantageously serves the dual function of: 1. concentrating the energy in the passing water stream; and 2 supporting a relatively greater number of smaller and stronger blades 16, which each have a lower aspect ratio.
  • In relation to the latter issue, the bending moment at the root is a function of the aspect ratio of the blade. For example, a blade with an aspect ratio of 8:1 will have a stress value in the root that is 16 times higher than the same blade with an aspect ratio of 4:1. In a known 3-blade rotor with a relatively small diameter hub, the blades can only have a limited chord length at the root due to the diameter restriction of the hub. This restriction of chord length means that the blade root thickness must be increased, to provide sufficient strength, over that otherwise required for an ideal foil section.
  • A relatively longer blade mounted to a relatively smaller hub also results in a lower apparent velocity for a given RPM and a lower torque radius.
  • A thicker root, especially in the lower ⅓rd of the blade, combined with the lower apparent velocity and the lower torque radius, results in a lowered contribution to the total power of such a (known) 3-blade rotor. This is due to the fact that the outer ⅓rd of the blade in the smaller hub/larger 3-blade configuration does 63% of the work. This is a combination of the swept area of the outer 30% of the blade, which constitutes 56% of the total surface area, and the inner 30% of the blade producing negligible power.
  • In contrast, the configuration of the rotor 10 (i.e. relatively larger hub 14, relatively shorter blades 16, relatively large number of blades 16) redirects and concentrates the fluid flow in the inner ⅔ region and accelerates it through the outer ⅓rd region where 100% of the power can be extracted. This advantageously means that the blades 16 are operating at maximum capacity, while also experiencing a lower stress loading.
  • Put another way, the D2:D1 ratio of the rotor 10 places the blades 16 in a zone of acceleration around the hub 12 with an ideal blade length for the blades 16 to operate in that zone. If the blades are too long relative to the hub diameter then the blades tips instead operate in a region with no fluid acceleration and therefore do not contribute positive torque.
  • FIG. 3 shows a hydro-powered electricity generator 30 with a second embodiment of rotor 32. The rotor 32 has a hub 34 and ten blades 36. FIG. 3 also shows blade root mounting beams 38, a blade mounting hub 40, a fixed main spindle 42, a drive shaft 44, a gear box 46, a support beam 48, a water seal 50, bearings 52 and a rotary electrical generator 54. The beam 48 is used to connect the generator 30 to a floating deployment rig (not shown).
  • Also shown on FIG. 3 is radius R, being the profile radius hub 34 in the region where the hub 34 and the blades 36 are connected. In the preferred configuration shown, the radius R is ⅙ the radius of the hub 34. This particular ratio maximises flow acceleration while avoiding turbulence.
  • One preferred form of the generator 30 has the following specifications:
  • Hub diameter D1: 2.4 meters
  • Blade tip diameter D2: 4.8 to 3.6 meters
  • Power generation range: 50 to 300 kWs
  • Flow velocity range: 1.2 to 4.2 m/sec
  • Blade tip diameter to hub diameter ratio: 2:1 to 1.5:1
  • Another preferred form of the generator 30 has the following specifications:
  • Hub diameter D1: 20 meters
  • Blade tip diameter D2: 32 to 30 meters
  • Power generation range: 0.5 to 5 MWs
  • Flow velocity range: 1.2 to 4.0 m/sec
  • Blade tip diameter to hub diameter ratio: 1.6:1 to 1.5:1
  • There are several advantages for hydro-powered generators due to the (relatively larger) diameter hub to (relatively smaller) diameter blade ratios described above.
  • Firstly, the energy in the fluid stream is concentrated and accelerated across a set of small blades, which improves the efficiency of the rotor.
  • Secondly, the total volume of the multiple (e.g. 7) smaller blades is less than the volume of a small number of (e.g. 3) large blades, which lowers manufacturing cost.
  • Thirdly, the smaller blades have a lower aspect ratio, which equates to a lower bending moment in the blade root, and a lower probability of blade breakage.
  • Fourthly, the incident velocity and the incident angle of the flow onto the smaller blades is closer to a uniform value across the span of the blades. This equates to near zero twist in the blade across its span, and allows the blades to be articulated in pitch control without any performance losses induced by blade twist. Further, the ability to adjust the pitch during operation means the rotor can be run at a constant rpm independent of the flow stream velocity. This allows the generator to be run at a constant rpm connected directly to the electrical grid thereby negating the cost of an electrical frequency inverter drive system.
  • Fifthly, rotors operating in fast flowing tidal flows are subject to high levels of turbulence in the stream. The action of the flow acceleration of the water around the larger hub reduces the level of turbulence into the blade region. This improves the survivability of the blades in highly turbulence environments.
  • Although the invention has been described with reference to preferred embodiments, it will be appreciated by person skilled in the art that the invention may be embodied in other forms.

Claims (6)

1. A rotor for a hydro-powered electricity generator, the rotor including:
a hub with a circular cross sectional shape and a longitudinal rotational axis, a plurality of blades, each having a proximal root and a distal tip, each of the blade roots being mounted to the hub at the widest part thereof,
wherein the ratio between the diameter of the tips of the blades to the diameter of the widest part of the hub is less than about 2:1.
2. The rotor as claimed in claim 1, wherein the ratio between the diameter of the tips of the blades to the diameter of the widest part of the hub is between about 1.2:1 and 2:1.
3. The rotor as claimed in claim 1, wherein the ratio between the diameter of the tips of the blades to the diameter of the widest part of the hub is about 1.5:1 or about 1.6:1.
4. The rotor as claimed in claim 1, wherein the diameter of the tips of the blades is between 3.6 and 4.8 metres and the diameter of the widest part of the hub is 2.4 metres.
5. The rotor as claimed in claim 1, wherein the diameter of the tips of the blades is between 30 and 32 metres and the diameter of the widest part of the hub is 20 metres.
6. The rotor as claimed in claim 1, wherein the profile radius of the hub surface, in the region where each of the blade roots are mounted to the hub, is between ⅙th of and equal to the radius of the widest part of the hub.
US15/558,922 2015-03-17 2016-03-16 A rotor for an electricity generator Abandoned US20180073367A1 (en)

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AU2015900950A AU2015900950A0 (en) 2015-03-17 A rotor for an electricity generator
AU2015900950 2015-03-17
PCT/AU2016/000091 WO2016145477A1 (en) 2015-03-17 2016-03-16 A rotor for an electricity generator

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PCT/AU2016/000091 A-371-Of-International WO2016145477A1 (en) 2015-03-17 2016-03-16 A rotor for an electricity generator
US17/079,049 Continuation US11573559B2 (en) 2015-03-17 2020-10-23 Techniques for generating and performing analytical instrument test plans

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US17/078,049 Continuation US11767762B2 (en) 2015-03-17 2020-10-22 Rotor for an electricity generator
US17/079,049 Continuation US11573559B2 (en) 2015-03-17 2020-10-23 Techniques for generating and performing analytical instrument test plans
US18/455,587 Continuation US20230399952A1 (en) 2015-03-17 2023-08-24 Rotor for an electricity generator

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US18/455,587 Pending US20230399952A1 (en) 2015-03-17 2023-08-24 Rotor for an electricity generator

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US20230278685A1 (en) * 2020-05-21 2023-09-07 Korea Shipbuilding & Offshore Engineering Co., Ltd. Variable-pitch propeller having optimal hub-to-tip diameter ratio

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US11286779B2 (en) 2020-06-03 2022-03-29 Honeywell International Inc. Characteristic distribution for rotor blade of booster rotor
US20230041561A1 (en) * 2021-07-20 2023-02-09 Robert J Evans Systems and Methods for a Hydrokinetic Micro Powerplant

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KR102471788B1 (en) 2022-11-28
WO2016145477A1 (en) 2016-09-22
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BR112017019775A2 (en) 2018-05-15
AU2016232976B2 (en) 2017-12-07
CN106460769A (en) 2017-02-22
HK1249771A1 (en) 2018-11-09
EP3271570A4 (en) 2018-10-31
EP3271570A1 (en) 2018-01-24
AU2018201500A1 (en) 2018-04-19
US11767762B2 (en) 2023-09-26
PH12017501682A1 (en) 2018-03-12
SG11201603713TA (en) 2016-10-28
JP6954739B2 (en) 2021-10-27
US20230399952A1 (en) 2023-12-14
JP2018507973A (en) 2018-03-22
NZ736092A (en) 2019-03-29
KR20180004713A (en) 2018-01-12
ZA201706827B (en) 2021-04-28
SG10202006344QA (en) 2020-08-28
CA3017762A1 (en) 2016-09-22
AU2016232976A1 (en) 2016-12-15
CL2017002352A1 (en) 2018-05-11

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